Multi-speed transmission

ABSTRACT

A transmission is provided having an input member, an output member, four planetary gear sets, a plurality of coupling members and a plurality of torque transmitting devices. Each of the planetary gear sets includes first, second and third members. The torque transmitting devices may include clutches and brakes.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application claims the benefit of U.S. Provisional Application No.60/913,255, filed on Apr. 20, 2007. The disclosure of the aboveapplication is incorporated herein by reference.

FIELD

The invention relates generally to a multiple speed transmission havinga plurality of planetary gear sets and a plurality of torquetransmitting devices and more particularly to a transmission havingeight or more speeds, four planetary gear sets and a plurality of torquetransmitting devices.

BACKGROUND

The statements in this section merely provide background informationrelated to the present disclosure and may or may not constitute priorart.

A typical multiple speed transmission uses a combination of frictionclutches, planetary gear arrangements and fixed interconnections toachieve a plurality of gear ratios. The number and physical arrangementof the planetary gear sets, generally, are dictated by packaging, costand desired speed ratios.

While current transmissions achieve their intended purpose, the need fornew and improved transmission configurations which exhibit improvedperformance, especially from the standpoints of efficiency,responsiveness and smoothness and improved packaging, primarily reducedsize and weight, is essentially constant. Accordingly, there is a needfor an improved, cost-effective, compact multiple speed transmission.

SUMMARY

A transmission is provided having an input member, an output member,four planetary gear sets, a plurality of coupling members and aplurality of torque transmitting devices. Each of the planetary gearsets includes first, second and third members. The torque transmittingdevices are for example clutches and brakes.

An embodiment of the transmission includes an input member, an outputmember, first, second, third and fourth planetary gear sets each havingfirst, second and third members, a first interconnecting membercontinuously interconnecting the first member of the first planetarygear set with a stationary element, a second interconnecting membercontinuously interconnecting the third member of the first planetarygear set with the first member of the second planetary gear set, a thirdinterconnecting member continuously interconnecting the third member ofthe second planetary gear set with the third member of the thirdplanetary gear set, a fourth interconnecting member continuouslyinterconnecting the first member of the third planetary gear set withthe third member of the fourth planetary gear set, and a fifthinterconnecting member continuously interconnecting the second member ofthe third planetary gear set with the second member of the fourthplanetary gear set. Five torque-transmitting mechanisms are selectivelyengageable to interconnect one of the first, second, and third memberswith another of the first, second, third members, and the stationaryelement. The torque-transmitting mechanisms are selectively engageablein combinations of at least two to establish at least eight forwardspeed ratios and at least one reverse speed ratio between the inputmember and the output member.

In one aspect of the present invention, a first of the five torquetransmitting mechanisms is selectively engageable to interconnect thesecond member of the first planetary gear set with the third member ofthe second planetary gear set.

In another aspect of the present invention, a second of the five torquetransmitting mechanisms is selectively engageable to interconnect thethird member of the first planetary gear set with the third member ofthe second planetary gear set.

In yet another aspect of the present invention, a third of the fivetorque transmitting mechanisms is selectively engageable to interconnectthe second member of the first planetary gear set with the first memberof the fourth planetary gear set.

In yet another aspect of the present invention, a fourth of the fivetorque transmitting mechanisms is selectively engageable to interconnectthe second member of the second planetary gear set with the outputmember.

In yet another aspect of the present invention, a fifth of the fivetorque transmitting mechanisms is selectively engageable to interconnectthe third member of the fourth planetary gear set with the stationaryelement.

In yet another aspect of the present invention, the first member of thefirst planetary gear set is a sun gear, the second member of the firstplanetary gear set is a carrier member, the third member of the firstplanetary gear set is a ring gear, the first member of the secondplanetary gear set is a sun gear, the second member of the secondplanetary gear set is a carrier member, the third member of the secondplanetary gear set is a ring gear, the first member of the thirdplanetary gear set is a ring gear, the second member of the thirdplanetary gear set is a carrier member, the third member of the thirdplanetary gear set is a sun gear, the first member of the fourthplanetary gear set is a carrier member, the second member of the fourthplanetary gear set is a ring gear, and the third member of the fourthplanetary gear set is a sun gear.

Still another embodiment of the transmission of the present inventionincludes an input member, an output member, first, second, third andfourth planetary gear sets each having first, second and third members,wherein the input member is continuously interconnected with the secondmember of the first planetary gear set and wherein the output member iscontinuously interconnected with the second member of the thirdplanetary gear set, a first interconnecting member continuouslyinterconnecting the first member of the first planetary gear set with astationary element, a second interconnecting member continuouslyinterconnecting the third member of the first planetary gear set withthe first member of the second planetary gear set, a thirdinterconnecting member continuously interconnecting the third member ofthe second planetary gear set with the third member of the thirdplanetary gear set, a fourth interconnecting member continuouslyinterconnecting the first member of the third planetary gear set withthe third member of the fourth planetary gear set, and a fifthinterconnecting member continuously interconnecting the second member ofthe third planetary gear set with the second member of the fourthplanetary gear set. A first torque transmitting mechanism is selectivelyengageable to interconnect the second member of the first planetary gearset with the third member of the second planetary gear set. A secondtorque transmitting mechanism is selectively engageable to interconnectthe third member of the first planetary gear set with the third memberof the second planetary gear set. A third torque transmitting mechanismis selectively engageable to interconnect the second member of the firstplanetary gear set with the first member of the fourth planetary gearset. A fourth torque transmitting mechanism is selectively engageable tointerconnect the second member of the second planetary gear set with theoutput member. A fifth torque transmitting mechanism is selectivelyengageable to interconnect the third member of the fourth planetary gearset with the stationary element. The torque-transmitting mechanisms areselectively engageable in combinations of at least two to establish atleast eight forward speed ratios and at least one reverse speed ratiobetween the input member and the output member.

In one aspect of the present invention, the first member of the firstplanetary gear set is a sun gear, the second member of the firstplanetary gear set is a carrier member, the third member of the firstplanetary gear set is a ring gear, the first member of the secondplanetary gear set is a sun gear, the second member of the secondplanetary gear set is a carrier member, the third member of the secondplanetary gear set is a ring gear, the first member of the thirdplanetary gear set is a ring gear, the second member of the thirdplanetary gear set is a carrier member, the third member of the thirdplanetary gear set is a sun gear, the first member of the fourthplanetary gear set is a carrier member, the second member of the fourthplanetary gear set is a ring gear, and the third member of the fourthplanetary gear set is a sun gear.

Further objects, aspects and advantages of the present invention willbecome apparent by reference to the following description and appendeddrawings wherein like reference numbers refer to the same component,element or feature.

DRAWINGS

The drawings described herein are for illustration purposes only and arenot intended to limit the scope of the present disclosure in any way.

FIG. 1 is a lever diagram of an embodiment of an eight speedtransmission according to the present invention;

FIG. 2 is a diagrammatic view of an embodiment of an eight speedtransmission according to the present invention; and

FIG. 3 is a truth table presenting the state of engagement of thevarious torque transmitting clutches and brakes in each of the availableforward and reverse speeds or gear ratios of the transmissionillustrated in FIGS. 1 and 2.

FIG. 4 is a lever diagram of another embodiment of an eight speedtransmission according to the present invention;

FIG. 5 is a diagrammatic view of another embodiment of an eight speedtransmission according to the present invention;

FIG. 6 is a truth table presenting the state of engagement of thevarious torque transmitting clutches and brakes in each of the availableforward and reverse speeds or gear ratios of the transmissionillustrated in FIGS. 4 and 5;

FIG. 7 is a lever diagram of another embodiment of an eight speedtransmission according to the present invention;

FIG. 8 is a diagrammatic view of another embodiment of an eight speedtransmission according to the present invention; and

FIG. 9 is a truth table presenting the state of engagement of thevarious torque transmitting clutches and brakes in each of the availableforward and reverse speeds or gear ratios of the transmissionillustrated in FIGS. 7 and 8.

DETAILED DESCRIPTION

The following description is merely exemplary in nature and is notintended to limit the present disclosure, application, or uses.

At the outset, it should be appreciated that the first, second, and thethird embodiments of the eight speed automatic transmission of thepresent invention have an arrangement of permanent mechanicalconnections between the elements of the four planetary gear sets incommon. These mechanical connections generically link or relate thethree transmission embodiments. A first component or element of a firstplanetary gear set is permanently coupled to a ground. A secondcomponent or element of the first planetary gear set is permanentlycoupled to a second component or element of a second planetary gear set.A first component or element of the second planetary gear set ispermanently coupled to a first component or element of a third planetarygear set. A second component or element of the third planetary gear setis permanently coupled to a second component or element of a fourthplanetary gear set. Finally, a third component or element of the thirdplanetary gear set is permanently coupled to a third component orelement of the fourth planetary gear set.

Referring now to FIG. 1, an embodiment of an eight speed transmission 10is illustrated in a lever diagram format. A lever diagram is a schematicrepresentation of the components of a mechanical device such as anautomatic transmission. Each individual lever represents a planetarygear set wherein the three basic mechanical components of the planetarygear are each represented by a node. Therefore, a single lever containsthree nodes: one for the sun gear, one for the planet gear carrier, andone for the ring gear. The relative length between the nodes of eachlever can be used to represent the ring-to-sun ratio of each respectivegear set. These lever ratios, in turn, are used to vary the gear ratiosof the transmission in order to achieve an appropriate ratios and ratioprogression. Mechanical couplings or interconnections between the nodesof the various planetary gear sets are illustrated by thin, horizontallines and torque transmitting devices such as clutches and brakes arepresented as interleaved fingers. If the device is a brake, one set ofthe fingers is grounded. Further explanation of the format, purpose anduse of lever diagrams can be found in SAE Paper 810102, “The LeverAnalogy: A New Tool in Transmission Analysis” by Benford and Leisingwhich is hereby fully incorporated by reference.

The transmission 10 includes an input shaft or member 12, a firstplanetary gear set 14 having three nodes: a first node 14A, a secondnode 14B and a third node 14C, a second planetary gear set 16 havingthree nodes: a first node 16A, a second node 16B and a third node 16C, athird planetary gear set 18 having three nodes: a first node 18A, asecond node 18B and a third node 18C, a fourth planetary gear set 20having three nodes: a first node 20A, a second node 20B and a third node20C and an output shaft or member 22.

The input 12 is coupled to the third node 14C of the first planetarygear set. The output 22 is coupled to the third node 18C of the thirdplanetary gear set 18. The first node 14A of the first planetary gearset 14 is coupled to a ground or transmission housing 40. The secondnode 14B of the first planetary gear set 14 is coupled to the secondnode 16B of the second planetary gear set 16. The first node 16A of thesecond planetary gear set 16 is coupled to the first node 18A of thethird planetary gear set 18. The second node 18B of the third planetarygear set 18 is coupled to a second node 20B of the fourth planetary gearset 20. The third node 18C of the third planetary gear set 18 is coupledto the third node 20C of the fourth planetary gear set 20.

A first clutch 26 selectively connects the third node 14C of the firstplanetary gear set 14 to the third node 16C of the second planetary gearset 16. A second clutch 28 selectively connects the third node 16C ofthe second planetary gear set 16 to the second node 18B of the thirdplanetary gear set 18. A third clutch 30 selectively connects the input12 and the third node 14C of the first planetary gear set 14 to thefirst node 20A of the fourth planetary gear set 20. A fourth clutch 32selectively connects the second node 16B of the second planetary gearset 16 to the first node 20A of the fourth planetary gear set 20. Afirst brake 34 selectively connects the second node 18B of the thirdplanetary gear set 18 to the ground or transmission housing 40.

Referring now to FIG. 2, a stick diagram presents a schematic layout ofthe embodiment of the eight speed transmission 10 according to thepresent invention. In FIG. 2, the numbering from the lever diagram ofFIG. 1 is carried over. The clutches, brakes and couplings arecorrespondingly presented whereas the nodes of the planetary gear setsnow appear as components of planetary gear sets such as sun gears, ringgears, planet gears and planet gear carriers.

For example, planetary gear set 14 is a planetary gear set that includesa sun gear member 14A, a planet gear carrier member 14C and a ring gearmember 14B. Sun gear member 14A is connected for common rotation with afirst shaft or interconnecting member 42 which is fixed to the ground ortransmission housing 40. Ring gear member 14B is connected to a secondshaft or interconnecting member 44. The planet gear carrier member 14Crotatably supports a set of planet gears 14D (only one shown) and isconnected for common rotation with a third shaft or interconnectingmember 46 and the input 12. Planet gears 14D are configured to intermeshwith sun gear member 14A and ring gear member 14B.

The input shaft or member 12 is continuously connected to an engine (notshown) or to a turbine of a torque converter (not shown). The outputshaft or member 22 is continuously connected with the final drive unitor transfer case (not shown).

Planetary gear set 16 is a planetary gear set that includes a sun gearmember 16B, a planet carrier member 16C that rotatably supports a set ofplanet gears 16D and a ring gear member 16A. Sun gear member 16B isconnected for common rotation with the second interconnecting member 44and a fourth shaft or interconnecting member 48. Planet carrier member16C is connected for common rotation with a fifth shaft orinterconnecting member 50. Ring gear member 16A is connected for commonrotation with a sixth shaft or interconnecting member 52. Planet gears16D are configured to intermesh with both sun gear member 16C and ringgear member 16A.

Planetary gear set 18 is a planetary gear set that includes a sun gearmember 18B, a ring gear member 18A and a planet carrier member 18C thatrotatably supports a set of planet gears 18D. Sun gear member 18B isconnected for common rotation with a seventh shaft or interconnectingmember 54 and to an eighth shaft or interconnecting member 56. Ring gearmember 18A is connected for common rotation with the sixthinterconnecting member 52. Planet carrier member 18C is connected forcommon rotation with a ninth shaft or interconnecting member 58. Planetgears 18D are configured to intermesh with both sun gear member 18B andring gear member 18A.

Planetary gear set 20 is a planetary gear set that includes a sun gearmember 20A, a ring gear member 20B and a planet carrier member 20C thatrotatably supports a set of planet gears 20D. Sun gear member 20A isconnected for common rotation with a tenth shaft or interconnectingmember 60. Ring gear member 20B is connected for common rotation withthe seventh interconnecting member 54. Planet carrier member 20C isconnected for common rotation with the ninth interconnecting member 58and to the output 22. Planet gears 20D are configured to intermesh withboth sun gear member 20A and ring gear member 20B.

The torque-transmitting mechanisms or clutches 26, 28, 30, and 32 andthe brake 34 allow for selective interconnection of the shafts orinterconnecting members, members of the planetary gear sets and thehousing. For example, the first clutch 26 is selectively engageable toconnect the third interconnecting member 46 to the fifth interconnectingmember 50. The second clutch 28 is selectively engageable to connect thefifth interconnecting member 50 to the eighth interconnecting member 56.The third clutch 30 is selectively engageable to connect the input 12 tothe tenth interconnecting member 60. The fourth clutch 32 is selectivelyengageable to connect the fourth interconnecting member 48 to the tenthinterconnecting member 60. The first brake 34 is selectively engageableto connect the eighth interconnecting member 56 to the ground ortransmission housing 40 to restrict rotation of the eighthinterconnecting member 56 relative to the housing 40.

Referring now to FIGS. 2 and 3, the operation of the embodiment of theeight speed transmission 10 will be described. It will be appreciatedthat transmission 10 is capable of transmitting torque from the inputshaft or member 12 to the output shaft or member 22 in at least eightforward speed or torque ratios and at least one reverse speed or torqueratio. Each forward and reverse speed or torque ratio is attained byengagement of one or more of the torque-transmitting mechanisms (i.e.first clutch 26, second clutch 28, third clutch 30, fourth clutch 32,and first brake 34), as will be explained below. FIG. 3 is a truth tablepresenting the various combinations of torque-transmitting mechanismsthat are activated or engaged to achieve the various gear states. Actualnumerical gear ratios of the various gear states are also presentedalthough it should be appreciated that these numerical values areexemplary only and that they may be adjusted over significant ranges toaccommodate various applications and operational criteria of thetransmission 10. An example of the gear ratios that may be obtainedusing the embodiments of the present invention are also shown in FIG. 3.Of course, other gear ratios are achievable depending on the geardiameter, gear teeth count and gear configuration selected.

To establish reverse gear, the first brake 34 and the second clutch 28are engaged or activated. The first brake 34 connects the eighthinterconnecting member 56 to the ground or transmission housing 40 torestrict rotation of the eighth interconnecting member 56 relative tothe housing 40. The second clutch 28 connects the fifth interconnectingmember 50 to the eighth interconnecting member 56. Likewise, the eightforward ratios are achieved through different combinations of clutchengagement, as shown in FIG. 3.

It will be appreciated that the foregoing explanation of operation andgear states of the eight speed transmission 10 assumes, first of all,that all the clutches and the brake not specifically referenced in agiven gear state are inactive or disengaged and, second of all, thatduring gear shifts, i.e., changes of gear state, between at leastadjacent gear states, a clutch or brake engaged or activated in bothgear states will remain engaged or activated.

Referring now to FIG. 4, another embodiment of a transmission isillustrated and referenced by reference numeral 100. Transmission 100includes an input shaft or member 112, a first planetary gear set 114having three nodes: a first node 114A, a second node 114B and a thirdnode 114C, a second planetary gear set 116 having three nodes: a firstnode 116A, a second node 116B and a third node 116C, a third planetarygear set 118 having three nodes: a first node 118A, a second node 118Band a third node 118C, a fourth planetary gear set 120 having threenodes: a first node 120A, a second node 120B and a third node 120C andan output shaft or member 122.

The input 112 is coupled to the third node 114C of the first planetarygear set 114. The output 122 is coupled to the third node 118C of thethird planetary gear set 118. The first node 114A of the first planetarygear set 114 is coupled to a ground or transmission housing 140. Thesecond node 114B of the first planetary gear set 114 is coupled to thesecond node 116B of the second planetary gear set 116. The first node116A of the second planetary gear set 116 is coupled to the first node118A of the third planetary gear set 118. The second node 118B of thethird planetary gear set 118 is coupled to a second node 120B of thefourth planetary gear set 120. The third node 118C of the thirdplanetary gear set 118 is coupled to the third node 120C of the fourthplanetary gear set 120.

A first clutch 126 selectively connects the third node 114C of the firstplanetary gear set 114 to the first node 120A of the fourth planetarygear set 120. A second clutch 128 selectively connects the third node116C of the second planetary gear set 116 to the third node 118C of thethird planetary gear set 118 and to the output 122. A third clutch 130selectively connects the third node 114C of the first planetary gear set114 to the first node 116A of the second planetary gear set 116. Afourth clutch 132 selectively connects the second node 114B of the firstplanetary gear set 114 and the second node 116B of the second planetarygear set 116 to the first node 116A of the second planetary gear set116. A first brake 134 selectively connects the second node 120B of thefourth planetary gear set 120 to the ground or transmission housing 140.

Referring now to FIG. 5, a stick diagram presents a schematic layout ofthe embodiment of the eight speed transmission 100 according to thepresent invention. In FIG. 5, the numbering from the lever diagram ofFIG. 4 is carried over. The clutches, brakes and couplings arecorrespondingly presented whereas the nodes of the planetary gear setsnow appear as components of planetary gear sets such as sun gears, ringgears, planet gears and planet gear carriers.

For example, planetary gear set 114 is a planetary gear set thatincludes a sun gear member 114A, a planet gear carrier member 114C and aring gear member 114B. Sun gear member 114A is connected for commonrotation with a first shaft or interconnecting member 142 which ispermanently connected to the ground 140. Ring gear member 114B isconnected to a second shaft or interconnecting member 144. The planetgear carrier member 114C rotatably supports a set of planet gears 114D(only one shown) and is connected for common rotation with a third shaftor interconnecting member 146 and the input 112. Planet gears 114D areconfigured to intermesh with sun gear member 114A and ring gear member114B.

The input shaft or member 112 is continuously connected to an engine(not shown) or to a turbine of a torque converter (not shown). Theoutput shaft or member 122 is continuously connected with the finaldrive unit or transfer case (not shown).

Planetary gear set 116 is a planetary gear set that includes a sun gearmember 116B, a planet carrier member 116C that rotatably supports a setof planet gears 116D and a ring gear member 116A. Sun gear member 116Bis connected for common rotation with the second interconnecting member144. Planet carrier member 116C is connected for common rotation with afourth shaft or interconnecting member 148. Ring gear member 116A isconnected for common rotation with a fifth shaft or interconnectingmember 150 and with a sixth shaft or interconnecting member 152. Planetgears 116D are configured to intermesh with both sun gear member 116Band ring gear member 116A.

Planetary gear set 118 is a planetary gear set that includes a sun gearmember 118A, a ring gear member 118B and a planet carrier member 118Cthat rotatably supports a set of planet gears 118D. Sun gear member 118Ais connected for common rotation with the sixth interconnecting member152. Ring gear member 118B is connected for common rotation with aseventh shaft or interconnecting member 154. Planet carrier member 118Cis connected for common rotation with an eighth shaft or interconnectingmember 156 and to the output 122. Planet gears 118D are configured tointermesh with both sun gear member 118A and ring gear member 118B.

Planetary gear set 120 is a planetary gear set that includes a sun gearmember 120B, a ring gear member 120C and a planet carrier member 120Athat rotatably supports a first set of planet gears 120D and a secondset of planet gears 120E. Sun gear member 120B is connected for commonrotation with the seventh interconnecting member 154 and to a ninthshaft or interconnecting member 158. Ring gear member 120C is connectedfor common rotation with the eighth interconnecting member 156. Planetcarrier member 120A is connected for common rotation with a tenth shaftor interconnecting member 160. The first planet gears 120D areconfigured to intermesh with the sun gear member 120B and the secondplanet gears 120E are configured to intermesh with the ring gear member120C. The first and second planet gears 120D and 120E are configured tointermesh with one another.

The torque-transmitting mechanisms or clutches 126, 128, 130, and 132and the brake 134 allow for selective interconnection of the shafts orinterconnecting members, members of the planetary gear sets and thehousing. For example, the first clutch 126 is selectively engageable toconnect the third interconnecting member 146 to the tenthinterconnecting member 160. The second clutch 128 is selectivelyengageable to connect the fourth interconnecting member 148 to theoutput 122. The third clutch 130 is selectively engageable to connectthe third interconnecting member 146 to the fifth interconnecting member150. The fourth clutch 132 is selectively engageable to connect thesecond interconnecting member 144 to the fifth interconnecting member150. The first brake 134 is selectively engageable to connect the ninthinterconnecting member 158 to the ground 140 to restrict rotation of theninth interconnecting member 158 relative to the ground 140.

Referring now to FIGS. 5 and 6, the operation of the embodiment of theeight speed transmission 100 will be described. It will be appreciatedthat the transmission 100 is capable of transmitting torque from theinput shaft or member 112 to the output shaft or member 122 in at leasteight forward speeds or torque ratios and at least one reverse speed ortorque ratio. Each forward and reverse speed or torque ratio is attainedby engagement of one or more of the torque-transmitting mechanisms (i.e.first clutch 126, second clutch 128, third clutch 130, fourth clutch132, and first brake 134), as will be explained below. FIG. 6 is a truthtable presenting the various combinations of torque-transmittingmechanisms that are activated or engaged to achieve the various gearstates. Actual numerical gear ratios of the various gear states are alsopresented although it should be appreciated that these numerical valuesare exemplary only and that they may be adjusted over significant rangesto accommodate various applications and operational criteria of thetransmission 100. An example of the gear ratios that may be obtainedusing the embodiments of the present invention are also shown in FIG. 6.Of course, other gear ratios are achievable depending on the geardiameter, gear teeth count and gear configuration selected.

To establish reverse gear, the first brake 134 and the second clutch 128are engaged or activated. The first brake 134 connects the ninthinterconnecting member 158 to the ground 140 to restrict rotation of theninth interconnecting member 158 relative to the ground 140. The secondclutch 128 connects the fourth interconnecting member 148 to the output122. Likewise, the eight forward ratios are achieved through differentcombinations of clutch and brake engagement, as shown in FIG. 6.

It will be appreciated that the foregoing explanation of operation andgear states of the eight speed transmission 100 assumes, first of all,that all clutches and brakes not specifically referenced in a given gearstate are inactive or disengaged and, second of all, that during gearshifts, i.e., changes of gear state, between at least adjacent gearstates, a clutch or brake engaged or activated in both gear states willremain engaged or activated.

Referring now to FIG. 7, another embodiment of a transmission isillustrated and referenced by reference numeral 200. Transmission 200includes an input shaft or member 212, a first planetary gear set 214having three nodes: a first node 214A, a second node 214B and a thirdnode 214C, a second planetary gear set 216 having three nodes: a firstnode 216A, a second node 216B and a third node 216C, a third planetarygear set 218 having three nodes: a first node 218A, a second node 218Band a third node 218C, a fourth planetary gear set 220 having threenodes: a first node 220A, a second node 220B and a third node 220C andan output shaft or member 222.

The input 212 is coupled to the third node 214C of the first planetarygear set 214. The output 222 is coupled to the third node 220C of thefourth planetary gear set 220. The first node 214A of the firstplanetary gear set 214 is coupled to a ground or transmission housing240. The second node 214B of the first planetary gear set 214 is coupledto the second node 216B of the second planetary gear set 216. The firstnode 216A of the second planetary gear set 216 is coupled to the firstnode 218A of the third planetary gear set 218. The second node 218B ofthe third planetary gear set 218 is coupled to a second node 220B of thefourth planetary gear set 220. The third node 218C of the thirdplanetary gear set 218 is coupled to the third node 220C of the fourthplanetary gear set 220.

A first clutch 226 selectively connects the input 212 and the third node214C of the first planetary gear set 214 to the first node 216A of thesecond planetary gear set 216. A second clutch 228 selectively connectsthe third node 216C of the second planetary gear set 216 to the secondnode 218B of the third planetary gear set 218. A third clutch 230selectively connects the input 212 and the third node 214C of the firstplanetary gear set 214 to the second node 218B of the third planetarygear set 218. A fourth clutch 232 selectively connects the second node216B of the second planetary gear set 216 to the second node 218B of thethird planetary gear set 218. A first brake 234 selectively connects thefirst node 220A of the fourth planetary gear set 220 to the ground ortransmission housing 240.

Referring now to FIG. 8, a stick diagram presents a schematic layout ofthe embodiment of the eight speed transmission 200 according to thepresent invention. In FIG. 8, the numbering from the lever diagram ofFIG. 7 is carried over. The clutches, brakes and couplings arecorrespondingly presented whereas the nodes of the planetary gear setsnow appear as components of planetary gear sets such as sun gears, ringgears, planet gears and planet gear carriers.

For example, planetary gear set 214 is a planetary gear set thatincludes a sun gear member 214A, a planet gear carrier member 214C and aring gear member 214B. Sun gear member 214A is connected for commonrotation with a first shaft or interconnecting member 242 which ispermanently connected to the ground 240. Ring gear member 214B isconnected to a second shaft or interconnecting member 244. The planetgear carrier member 214C rotatably supports a set of planet gears 214D(only one shown) and is connected for common rotation with a third shaftor interconnecting member 246 and the input 212. Planet gears 214D areconfigured to intermesh with sun gear member 214A and ring gear member214B.

The input shaft or member 212 is continuously connected to an engine(not shown) or to a turbine of a torque converter (not shown). Theoutput shaft or member 222 is continuously connected with the finaldrive unit or transfer case (not shown).

Planetary gear set 216 is a planetary gear set that includes a sun gearmember 216B, a planet carrier member 216A that rotatably supports a setof planet gears 216D and a ring gear member 216C. Sun gear member 216Bis connected for common rotation with the second interconnecting member244 and with a fourth shaft or interconnecting member 248. Planetcarrier member 216A is connected for common rotation with a fifth shaftor interconnecting member 250. Ring gear member 216C is connected forcommon rotation with a sixth shaft or interconnecting member 252. Planetgears 216D are configured to intermesh with both sun gear member 216Band ring gear member 216C.

Planetary gear set 218 is a planetary gear set that includes a sun gearmember 218B, a ring gear member 218C and a planet carrier member 218Athat rotatably supports a set of planet gears 218D. Sun gear member 218Bis connected for common rotation with a seventh shaft or interconnectingmember 254 and to an eighth shaft or interconnecting member 256. Ringgear member 218C is connected for common rotation with a ninth shaft orinterconnecting member 258. Planet carrier member 218A is connected forcommon rotation with the fifth interconnecting member 250. Planet gears218D are configured to intermesh with both sun gear member 218B and ringgear member 218C.

Planetary gear set 220 is a planetary gear set that includes a sun gearmember 220B, a ring gear member 220A and a planet carrier member 220Cthat rotatably supports a set of planet gears 220D. Sun gear member 220Bis connected for common rotation with the eighth interconnecting member256. Ring gear member 220A is connected for common rotation with a tenthshaft or interconnecting member 260. Planet carrier member 220C isconnected for common rotation with the ninth interconnecting member 258and with the output 222. Planet gears 220D are configured to intermeshwith both sun gear member 220B and ring gear member 220A.

The torque-transmitting mechanisms or clutches 226, 228, 230, and 232and the brake 234 allow for selective interconnection of the shafts orinterconnecting members, members of the planetary gear sets and thehousing. For example, the first clutch 226 is selectively engageable toconnect the third interconnecting member 246 to the fifthinterconnecting member 250. The second clutch 228 is selectivelyengageable to connect the sixth interconnecting member 252 to theseventh interconnecting member 254. The third clutch 230 is selectivelyengageable to connect the input 212 to the seventh interconnectingmember 254. The fourth clutch 232 is selectively engageable to connectthe fourth interconnecting member 248 to the seventh interconnectingmember 254. The first brake 234 is selectively engageable to connect thetenth interconnecting member 260 to ground 240 to restrict rotation ofthe tenth interconnecting member 260 relative to the ground 240.

Referring now to FIGS. 8 and 9, the operation of the embodiment of theeight speed transmission 200 will be described. It will be appreciatedthat the transmission 200 is capable of transmitting torque from theinput shaft or member 212 to the output shaft or member 222 in at leasteight forward speeds or torque ratios and at least one reverse speed ortorque ratio. Each forward and reverse speed or torque ratio is attainedby engagement of one or more of the torque-transmitting mechanisms (i.e.first clutch 226, second clutch 228, third clutch 230, fourth clutch232, and first brake 234), as will be explained below. FIG. 9 is a truthtable presenting the various combinations of torque-transmittingmechanisms that are activated or engaged to achieve the various gearstates. Actual numerical gear ratios of the various gear states are alsopresented although it should be appreciated that these numerical valuesare exemplary only and that they may be adjusted over significant rangesto accommodate various applications and operational criteria of thetransmission 200. An example of the gear ratios that may be obtainedusing the embodiments of the present invention are also shown in FIG. 9.Of course, other gear ratios are achievable depending on the geardiameter, gear teeth count and gear configuration selected.

To establish reverse gear, the first brake 234 and the second clutch 228are engaged or activated. The first brake 234 connects the tenthinterconnecting member 260 to ground 240 to restrict rotation of thetenth interconnecting member 260 relative to the ground 240. The secondclutch 228 connects the sixth interconnecting member 252 to the seventhinterconnecting member 254. Likewise, the eight forward ratios areachieved through different combinations of clutch and brake engagement,as shown in FIG. 9.

It will be appreciated that the foregoing explanation of operation andgear states of the eight speed transmission 200 assumes, first of all,that all clutches and brakes not specifically referenced in a given gearstate are inactive or disengaged and, second of all, that during gearshifts, i.e., changes of gear state, between at least adjacent gearstates, a clutch or brake engaged or activated in both gear states willremain engaged or activated.

The description of the invention is merely exemplary in nature andvariations that do not depart from the gist of the invention areintended to be within the scope of the invention. Such variations arenot to be regarded as a departure from the spirit and scope of theinvention.

1. A transmission comprising: an input member; an output member; first,second, third and fourth planetary gear sets each having first, secondand third members, wherein the input member is continuouslyinterconnected with the second member of the first planetary gear setand the output member is continuously interconnected with the secondmember of the third planetary gear set; a first interconnecting membercontinuously interconnecting the first member of the first planetarygear set with a stationary element; a second interconnecting membercontinuously interconnecting the third member of the first planetarygear set with the first member of the second planetary gear set; a thirdinterconnecting member continuously interconnecting the third member ofthe second planetary gear set with the third member of the thirdplanetary gear set; a fourth interconnecting member continuouslyinterconnecting the first member of the third planetary gear set withthe third member of the fourth planetary gear set; a fifthinterconnecting member continuously interconnecting the second member ofthe third planetary gear set with the second member of the fourthplanetary gear set; and five torque-transmitting mechanisms selectivelyengageable to interconnect one of the first, second, and third memberswith another of the first, second, third members, and the stationaryelement; and wherein the torque-transmitting mechanisms are selectivelyengageable in combinations of at least two to establish at least eightforward speed ratios and at least one reverse speed ratio between theinput member and the output member.
 2. The transmission of claim 1wherein a first of the five torque transmitting mechanisms isselectively engageable to interconnect the second member of the firstplanetary gear set with the third member of the second planetary gearset.
 3. The transmission of claim 2 wherein a second of the five torquetransmitting mechanisms is selectively engageable to interconnect thethird member of the first planetary gear set with the third member ofthe second planetary gear set.
 4. The transmission of claim 3 wherein athird of the five torque transmitting mechanisms is selectivelyengageable to interconnect the second member of the first planetary gearset with the first member of the fourth planetary gear set.
 5. Thetransmission of claim 4 wherein a fourth of the five torque transmittingmechanisms is selectively engageable to interconnect the second memberof the second planetary gear set with the output member.
 6. Thetransmission of claim 5 wherein a fifth of the five torque transmittingmechanisms is selectively engageable to interconnect the first member ofthe third planetary gear set with the stationary element.
 7. Thetransmission of claim 1 wherein the first member of the first planetarygear set is a sun gear, the second member of the first planetary gearset is a carrier member, the third member of the first planetary gearset is a ring gear, the first member of the second planetary gear set isa sun gear, the second member of the second planetary gear set is acarrier member, the third member of the second planetary gear set is aring gear, the first member of the third planetary gear set is a ringgear, the second member of the third planetary gear set is a carriermember, the third member of the third planetary gear set is a sun gear,the first member of the fourth planetary gear set is a carrier member,the second member of the fourth planetary gear set is a ring gear, andthe third member of the fourth planetary gear set is a sun gear.
 8. Thetransmission of claim 1 wherein the five torque transmitting mechanismsinclude four brakes and one clutch.
 9. A transmission comprising: aninput member; an output member; first, second, third and fourthplanetary gear sets each having first, second and third members, whereinthe input member is continuously interconnected with the second memberof the first planetary gear set and wherein the output member iscontinuously interconnected with the second member of the thirdplanetary gear set; a first interconnecting member continuouslyinterconnecting the first member of the first planetary gear set with astationary element; a second interconnecting member continuouslyinterconnecting the third member of the first planetary gear set withthe first member of the second planetary gear set; a thirdinterconnecting member continuously interconnecting the third member ofthe second planetary gear set with the third member of the thirdplanetary gear set; a fourth interconnecting member continuouslyinterconnecting the first member of the third planetary gear set withthe third member of the fourth planetary gear set; a fifthinterconnecting member continuously interconnecting the second member ofthe third planetary gear set with the second member of the fourthplanetary gear set; a first torque transmitting mechanism selectivelyengageable to interconnect the second member of the first planetary gearset with the third member of the second planetary gear set; a secondtorque transmitting mechanism selectively engageable to interconnect thethird member of the first planetary gear set with the third member ofthe second planetary gear set; a third torque transmitting mechanismselectively engageable to interconnect the second member of the firstplanetary gear set with the first member of the fourth planetary gearset; a fourth torque transmitting mechanism selectively engageable tointerconnect the second member of the second planetary gear set with theoutput member; and a fifth torque transmitting mechanism selectivelyengageable to interconnect the first member of the third planetary gearset with the stationary element; and wherein the torque-transmittingmechanisms are selectively engageable in combinations of at least two toestablish at least eight forward speed ratios and at least one reversespeed ratio between the input member and the output member.
 10. Thetransmission of claim 9 wherein the first member of the first planetarygear set is a sun gear, the second member of the first planetary gearset is a carrier member, the third member of the first planetary gearset is a ring gear, the first member of the second planetary gear set isa sun gear, the second member of the second planetary gear set is acarrier member, the third member of the second planetary gear set is aring gear, the first member of the third planetary gear set is a ringgear, the second member of the third planetary gear set is a carriermember, the third member of the third planetary gear set is a sun gear,the first member of the fourth planetary gear set is a carrier member,the second member of the fourth planetary gear set is a ring gear, andthe third member of the fourth planetary gear set is a sun gear.
 11. Atransmission comprising: an input member; an output member; first,second, third and fourth planetary gear sets each having a sun gear, acarrier member, and a ring gear, wherein the input member iscontinuously interconnected with the carrier member of the firstplanetary gear set and wherein the output member is continuouslyinterconnected with the carrier member of the third planetary gear set;a first interconnecting member continuously interconnecting the sun gearof the first planetary gear set with a stationary element; a secondinterconnecting member continuously interconnecting the ring gear of thefirst planetary gear set with the sun gear of the second planetary gearset; a third interconnecting member continuously interconnecting thering gear of the second planetary gear set with the sun gear of thethird planetary gear set; a fourth interconnecting member continuouslyinterconnecting the ring gear of the third planetary gear set with thesun gear of the fourth planetary gear set; a fifth interconnectingmember continuously interconnecting the carrier member of the thirdplanetary gear set with the ring gear of the fourth planetary gear set;a first torque transmitting mechanism selectively engageable tointerconnect the carrier member of the first planetary gear set with thering gear of the second planetary gear set; a second torque transmittingmechanism selectively engageable to interconnect the ring gear of thefirst planetary gear set with the ring gear of the second planetary gearset; a third torque transmitting mechanism selectively engageable tointerconnect the carrier member of the first planetary gear set with thecarrier member of the fourth planetary gear set; a fourth torquetransmitting mechanism selectively engageable to interconnect thecarrier member of the second planetary gear set with the output member;and a fifth torque transmitting mechanism selectively engageable tointerconnect the ring gear of the third planetary gear set with thestationary element; and wherein the torque-transmitting mechanisms areselectively engageable in combinations of at least two to establish atleast eight forward speed ratios and at least one reverse speed ratiobetween the input member and the output member.